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MACHINE TOOL Original FiledJan. 12. 1928 11 Sheets-Sheet 10 Nov. 22, 1932.

W. F. GROENE ET AL MACHINE TOOL Original Fiied Jan. 12. 1928 11 Sheets-Shed 11 Reissued Nov. 22, 1932 UNITED STATES PATENT oFFlcE WILLIAM F. GBOENE AND HAROLD J. SIEKMAN N, CINCINNATI, OHIO, ASSIGNORS TO THE R. K. LE BLOND MACHINE TOO];- COMPANY, OF CINCINNATI, OHIO, A CORPORA- TION OF DELAWARE MACHINE TOOL Original No. 1,744,885, dated January 28,1930, Serial No. 246,314, filed. January 12, 1928. Application for reissue filed January 21, 1932.

Ourinvention relates to machine tools and more particularly to tools having a series of movmg working members having elements .thereon which must be moved with relation combined a single source of hydraulic energy arranged to deliver a constant volume, at

varying pressures, with aseries of pistons driven by the hydraulic energy, one piston driving each feeding device, and have arranged for an automatic control of such a power supply system.

Expressing our invention in more detail We provide a pump preferably of oil gear type, which delivers a constant volume of oil to the oil lines involved at any one valve setting. The oil is directed by a valve which is so arranged as to deliver a high volume and a low volume in forward or reverse direction through the lines. The lines are connected to a master cylinder in which a piston is moved in alternate directions, depending upon the direction of the oil imparted by the valve, and at a speed controlled by the volume of oil delivered. The master cylinder piston is connected to a cross head which has secured thereto-a series of pistons, one for each of a. primary series of oil cylinders, which oil cylinders deliver oil according to the thrust of the pistons therein to tool feeding or secondary cylinders, which tool feeding cylinders are operated to feed thetools into the work or withdraw them therefrom depending upon the direction of the piston in the secondary system. The use of across head and a mechanical connection tothe primary set of pistons is preferred by us to a hydraulic connection from the master cylinder to the primary cylinders, which would be generically similar.

aseries of members actuated Serial .No. 588,021.

As an application of this system of con trol, We illustrate a crank shaft lathe having by two cam shafts so that they move in an eccentric path with relation to the axes of the cam shafts.

This eccentric path, for each member, corresponds with the path traversed by a crank pin on a crank shaft to be cut, said shaft being mounted and rotated in the lathe. This double cam shaft operation has been suggested'prior to-our invention, and our improvement thereon consists in compensating for slight variations and twists in the members by floatingly connectingthe members to one of the cam shafts. The arrangement of cocentrics and tool holders permits of easy loading of the work and permits of a complete shielding of the lower eccentric from falling chips. I

We have devised a mode of mounting cutting tools and feeding them into work rela-.

tion with the crank pin of a shaft from both sides of the pin, each tool feeding or holding device being movable to and from the work from opposite sides. We accomplish the feed of the tool holders in a manner which prevents chatter and play,'since, according to our construction, the thrust against the one tool holder acts in opposition to the thrust enabled to bring the cutting tools to positive stops without injuring the power transmission mechanism, the stopping of the tools simply serving to build up pressure in the oil feedsystem. y

Ve haveprovided in various ways for the perfect operation of tools operating conjointly and simultaneously from opposite sides of all of the crank pins of a crank shaft, as will be hereinafter more specifically pointed out.

lVe illustrate our invention by a specific embodiment thereof exhibiting the various ating arm inventive features involved, which inventive features will be set forth in the claims that follow. I In the drawings:

Figure 1 is a diagrammatic view illustrati'ng the mode of operation of the illustrated embodiment of our invention.

, Figure 2 is a vertical cross section of the machine taken at the outside of the right hand cam driven member.

Figure 3 is a rear elevation of the machine.

Figure 4 is a front elevation of the machine, with the drive omitted.

Figure 5 is a central vertical section taken through with the hydraulic feed thereto partly in section.

Figure 6 is an elevation taken at the right hand end of Figure 5. i

Figure 7 is a section taken centrally through the flexible conduit device shown m Figure 5, which device is bent out of operating position into a straight line for purposes of illustration.

Figure 8 is a detail section taken through the mounting of the part shown in Figure 7 to the fixed portion of the machine. Figure- 9 is a longitudinal section taken through the master oil cylinder and its connections.

Figure 10 is shown in Figure trol connections.

Figurell is a detail front elevation of the automatic control cam and control lever system.

vFigure 12 is a detail 12-12 of Figure 11.

Figure 13 is a view in large scale'of some of the parts shown in Figure 11.

Figure 14 is a detail section on a larger scale than Figure 13 taken on the line 14-14 of Figure 13.

Figure 15 is a diagram of the drive connections for the lathe.

.Figure 16 '1 side elevation of the a side elevation of the parts 9 with the automatic consection on the line is a detai center one of the tool operating arms.

Figure 17 is a plan view of the tool operfor the center tool element of the machine.

' Figure 18 is arear elevation of the part shown in Figure '17, partly in section. Figure 19 is a perspective of one of the tool slide carriers or cam operated members, with its side plate removed.

' Figure 20 is a detail elevation of the upper bar of one of carrying frames, broken away a to show the gib adjustment.

Figure 21 is a front elevation of a complete carrying frame. 1

Figure 22 is a side elevation of one of the work supports.

Figure 23 is a front elevation of the same. Figure 24 is a side elevation of the right hand thrust frame. 7

one of the tool operating cylinders,

Figure 25 is a front elevation of the same. Figure 26 is a semi-diagrammatic plan view showing a crank shaft with the tools applied thereto.

The diagrammatic view in Figure 1 will illustrate the mode of operation of the machine and will primarily be described in full, using reference numerals which so far aspossible are carried into the other views. I

The oil gear type pump is shown at 1, as being driven by a motor '2. This pump has a valve structure at 3, by means of which the volume of oil delivered from the pump can be controlled, so as to stop the delivery, or direct it in opposite directions, with high volume or low volume in each direction. This valve and pump are procurable on the market, and have not been illustrated in detail.

The valve is operated by a rod 4a, which is connected to an arm 6f. This arm is part of a casting which includes a lever 4, and a notched plate 60. On the shaft 6y which supports this casting (see Figs. 13 and 14) is a sleeve on which is an arm 6d. The sleeve has an arcuate rib 6k and a shoulder tip. The arm 4 has a spring plunger 4f therein, that has a. notch 6m of the size of the arcuate rib 6k.

Then the spring plunger is depressed, the lever 4 can be moved without moving the sleeve and the arm 60?, if it is moved in such a direction as would depress the arm 6d.

Normally the lever-4 is actuated to start the mechanism and the control of the'movement of the casting thereafter is accomplished bv a master cam.

the arm 6f, and the-rod 4a.

A motor starting switch is housed in a box 5, through which power to the main drive motor 8 of the machine is supplied. A lever 6 having a sector plate 50. thereon operates the starting switch through a sector 56.

The notched plate portion 60 is so arranged that when a pin'or roller 60: at the lower end of the lever' 6 is moved to the right accompanying the movement of starting the motor 8, it will move into the notch 6b. When the lever 6 is then moved to full running position the pin So will lie in the .main notch of The cam thus operates the valve 4 through the medium of the casting,

ning condition the control system is operative.

The arm 6d is connected to a link 6e upon which link a spring 6g is applied, tendingto keep the arm 67 to the left and the valve in shut-0H condition.

The control cam is shown diagrammatically at 15, and engages a roller 6h on the end of the rod 66. This control cam is thus in a position to move the plate 60, when it is released for movement by the lever 6 and its pin 6a, but'not otherwise. The machine now being in operation, the lever 4 is moved to initiate the hydraulic flow, which cannot be done in a normal way, unless the motor is running. Abnormal or emergency move- -ments of the control valve without effecting the other mechanisms are provided for by The piston is connected to a cross head 14,

which is in turn connected to a seriesofpiston rods 13a for the pistons 11. These pistons move in cylinders 11a and act to force oil into or withdraw oil from the tool actuating oil cylinders.

WVc haveshown as a simpler diagramthan the specified mechanismemployed, a connec tion 16 between the cross head 14 and the master cam 15. The connection is intended to illustrate that the cam moves lengthwise, as the cross head is moved by the master piston.

The advantage of this single control system for all five of the pistons 11 is considerable, because all of them can be stopped, started, and movedfast or slow simultaneously by control from a single point.

A conduit 53is shown, which supplies the distributingsystem or secondary oil supply system composed of the cylinders 11a and their various connections with a full supply tool operating system.

ofoil at all times. This conduit is protected by a series of check valves 51. The conduit 54 is also indicated, constituting an overflow conduit for the secondary system, the system bein kept in its normal condition through the protection of the check valves indicated at 49.

Conduits 47 extending from the one end of each cylinder 11a supply oil under pressure from the several cylinders to the tool operating system. Conduits 50 supply oil from the other end of each cylinder to the Dependent upon which direction the pistons 11 are moved, the operating pistons of the tool operating sys tem will be moved in a corresponding direction.

The flexible'joints or conduits connecting the conduits 47 and 50 to the tool operating system are illustrated as in the form of two arms '37 and 39 connected rotatably by a tapered plug 38, as will be more specifically described, and coupled to the joints 26a and 33 at the two ends.

These flexible connections keep the two oil streams separate, so that one set of conduits acts as a return line when the other set is supplying the motive force to the tool operating pistons.

Thus theconduit 29 and the conduit 28, from the terminal connections 26a of the flexible conduit connections, are continuations in effect of the respective conduits 47 and 50.

Within the cylinders 24, which are supported on the movable tool slide carrying frames of-the machine, are the pistons 25, whose piston rods 25a connect to the operating arms 23. Rack bars 21 and 22 held slidably in the carrying frames are engaged by gear teeth on the ends of the arms 23, so that as the'arms are rocked by the action of the pistons 25, the rack bars will be moved either both of them toward acommon point, or both away from a common point. The rack bars serve'a's tool carrying slides, as will be noted.

The diagram illustrates the carrying frames at 19, the pivots of the tool operat- ,ing arms at 86, and the stop lugs for the tool slides or rack bars at 93. For the details of the carrying frames we refer to Figures 1921.

Referring first to Figures 2, 3 and 4, in which the assemblies .of the machine are shown, we have indicated the base of the machine at 55, from which the uprights or housings 56 extend.

Tie bars 57 and 58 extendacross the back and front of the machine and serve in mounting the thrust frames 105, as will be noted. The master cam shaft 59 extends between bearings near the upper ends of the housings, and is equipped with gears '60 and 60a on either end thereof. The lower master shaft 10 ismounted in bearings in the base and is equipped with gears 61 and 61d at either end (see diagram Fig. 15).

The two spindles of the machine noted at 69 have head plates 70 provided with holes 71 therein for bolting in place any suitable chucking device for gripping a crank shaft tobe operated upon.

Idler gears 63, 63a, mesh with the gears 60, 60a, and 61, 610, at each side of the machine. The spindles are equipped with gears 62-, 62a, which mesh with the. idlers 63 also.

The drive gear at 64, which derives its power from a motor 8 or any other desired source, meshes with an intermediate gear 65, which drives a cross shaft 67 equipped with gear 66 which meshes with 65. The crossshaft carries at its ends the gears 68 and 68a which drive the gears 61 and 61a, thus providing a positive. and matched drive for both ends of the cam shafts, and for both spindles.

l The master shafts or cam shafts, as indicated, are so arranged that the eccentric portions 59a and 1011 will correspondwith the eccentricity of the crankpin of the shaft to be operated upon. The shaft to be operated upon isso chucked as to revolve on its main bearings as a center, and the tool carrying frames on the master or cam shafts will move around so as to follow the movement of the crank shaft, that constitutes the work.

The carrying frames are built up .of a pair of side plates 7 6 and 77 bolted over top and bottom frame members 73 and 75 respectively. The bottom frame member has a bearing 74 to engage over the desired eccentric on the bottom master shaft. The upper ends or extension 79 of the two side plates contain holes 80 for the bearing pin connection to the selected eccentric of the upper master shaft. Rivets passed through holes 78 will be the preferred mode of securing the parts of the frames.

-Thus, a bearing pin 81' engages the end 84 of a yoke, and holds it between the two side plate extensions 79. The yoke, as at 82, engages over the selected eccentric on the mas ter shaft, the outer portion of the split-bearing over the eccentric being provided by the bearing cap 83.

tool slides.

-The space between the side plates of the" carrying frames is used for mounting the The slides are two in number and fit snugly between the side plates laterally. The slide 21 at the lower part of the frame bears on the plate 7 5, and the upper too-l slide QO'bears on thetop of the slide 21 and is held down by means of a gib, to bedescribed. The two slides have teeth 22 thereon, at the upper end, and means. for

holding cutting tools 20a and 2161/. at the lower end. The operating arm 23 is mounted on a stud or bearing pin 86, set into the two frame side plates, with its teeth 23 meshing with the teeth on the two rack bars.

The act of rocking the arm will cause the two slides to move either toward eaclrother or away from each other, thus bringing the two tools 20a and 21a toward the work, or away from the work. The load on either one of the tools will tend to resist the motion imparted to its slide by the gear, and the load on one tool is opposed to the load on the other, so that a balanced and non-chattering relationship is established.

The gib 87, mounted to bear against the upper slide and against the upper plate 7 3 of the tool slide carrying frame, serves as a stop for tool movement. Depending upon the po-' sitionof the gib lengthwise of its mounting (Fig. 20) it will engage the lug 93 of the slide 22. When the upper slide is stopped, the lower slide stops also.

The gib is held down against the upper slide by means of setscrews 89. Y The gib has a lug 96 thereon which lies in a socket or chamber in the upper frame plate 73,

said socket beinglarger than the lug. A set '92 is employed. It can be seen that this screw 92 will prevent the gib from moving when the lug 93 on the upper slide engages the gib. The lug 93 will preferably be a removable block of metal which can be changed to extend the limits of adjustability of the stop mechanism. 3

On the outer faces of the tool carrying frames *are mounted face plates 92 of hardened steel, said plates serving to contact with like bearing plates on a series of intermediate non-moving plates which interspace pairs of the tool'carrying frames of the device.

The central carrying frame is different from the others in this particular machine, being of double the width of the others and carrying more than one set of slides. It will be described below, but may be considered as a double frame, as compared to a pair of independent frames.

The intermediate plates (Figs. 23-25) are either mere bearing frames which engage (Fig. 4) which also act in the same manner as the notches in the tie bars.

One of the steady rest intermediateplates is illustrated at 94, having projections 94a, 94b, and 940. The projection 94a is set into the notch arranged for it in the tie bar 58.

The projection 94b is set in the notch in the tie bar 57 arranged for it, and the projection 94c lies in the spaces between the blocks 96 on the machine base. Bolts, 98a passing through holes 98 in the projections 94?) and 940 mount. the plate in place, the holes being slightly larger than the bolts. Set into each side of each of the projections are set screws 99, whose heads bear against the side walls of the notches in which the projections lie.

adjusting the set screws the plate can be very accurately centered and placed, after which the bolts are brought down tightly'so that the plate is firmly bound, and constitutes one of the frame members of the machine.

Hardened steel face plates 100 on the members 94 match and bear against the like plates on the carrying frames, as has been noted.

Clamps 101 mounted at the front intermediate portion of the members 94 serve to form bearings together with the plates, which bearings engage over the journal pin of the work to be supported or steadied. The

which ably hushed, and a swinging yoke 102 held to the plate 94 can be used to engage and hold down the clamps 101 in the several steady rests engaging lugs 104 on the clamps by means of set screws 103.

The steady rest plates are used intermediate the housings and at the two ends of the assembly and next'to the housings, thrust plates 105 (Figs. 24 and 25) are employed, have a like mounting to the steady rest plates, and have the face plates 106 on the inner sides thereof only. These plates 105 serve as end thrust members for the assembly, and will be formed as a right and left plate with the face plates or facings 106 on the in- I ner side.

The entire assembly, it will be noted, is excessively strong and rigid, presenting practically a solid block of metal across the machine so as to prevent side play to the greatest extent to the tollcarrying member and work steady rest plates. The whole structure is furthermore subject to adjustment.

By reference to Figs. 3, 4, 16,17, 18 and 26,

it will be noted that the central one of the carriers may be built in a multiple relation, so as to permit of checking the webs and .cutting the pins at the middle of the shaft to be turned.

The carrier in this case is wider than the other carriers, the lower tool slide is wider and there are two upper tool slides instead of one. The operating arm with its gear toothed end is a multiple construction instead of a single one as in the former instance, and it is required that an equalizing action be provided for in connection with the operation of operation on the balancer portion 127 of the the arm device, because of requirements for slight self-adjustment of the tools with relation to each other, and requirements .for com pensation in the case .that one side of the double structure would come up against its stop a slight interval before the other one.

The side plates being the same in the carriers, they are not specially described. The

lower tool slide, in the form of a wide bar,

with the rack teeth at its upper end, is shown at its lower end at 21 in Fig. 26, and carries three tools 111, held in adjusted position by the set screws 112. The upper tool slide bars each-having rack teeth and set side by side above the lower bar, are shown at 20a and 20b in Fig. 26.v

A-set of three tools is provided .for each of the upper slide bars, tools 132 and 134 for the two crank pins 126 and 128,-andthe tools 133, one on each slide bar, for doing the same shaft, making six tools in all of the two upper slide bars.

The tool arrangement on all of the slides together providefor the full turning operation required; They are shown in Fig. 26, as they willbe at the end of the feeding operation.

. are open at 121, so that the cross that a rapid traverse of the A comparison of the tool arrangement is given in Fig. 26 withthe arrangement in the other carriers. The upper and lower slide bars 20 and 21 are shown as equipped with the tools 111a and 132a. The tools operate to turn the cheek and fillet and the pin. Referring to the tools of one of the single carrying frames, the outer edge of the tools 132a perform the checking operation, and the rest of the tools 132a turn the fillet and twin part of the pin. The tool 111a turns the pin and overlaps the operation of the tools-132a, thus avoiding tool marks. 4

The operating arm in the instance of the special carriers, is formed of three elements 112, 113 and 114. The three are mounted and pivoted by a single pin 86a correspond.-

ing in location and function to the pins 86 heretofore described. The teeth on the ends of the arms are shown at 112a and 113a for the outer bars, each one of which engages one of the upper slidebars, and the teeth 114a for the inner arm which engage on the lower slide bar.

The arm ll4has on its outer-end a pin 117 on which is mounted with a moving lit a cross head 118, having its ends rounded to engage in bearings 119 on the outer ends of the two outer arms 112 and 113. The bearings 119 are fitted with bushings 120 having the cylindrical sockets in which the rounded ends of the cross head are seated, and these bushings head can slide as well and rock in each of the bearings 119.

A connector 122 forked at 123 whereby it is connected to an operating piston rod, is

secured to or formed as part of the central narrower structures of the single carriers except for their width and the two upper slide bars will each 'carry a lug to act against the sto s.

s stated with relation to the general diagram, it is desirable in a lathe of the type in question to be able to do'the working in a speedy as well as a very accurate manner, so

tools to working position, a fast roughing cut to turn the cheeks. followed by av slow feed when the tools are all in engagement with the pins themselves, is highly necessary. The rapid traverse should then apply to withdraw the tools, as the machine comes to a stop. By our invention we supply these various movements in an automatic manner in an operation which turnsjall of the crank pins at once.

bar 108, that 1s held p In Figs. 10 to 14, and in the front view in Fig. 4, is shown the specific embodiment, differing, as has been noted, from the diagram of Fig. 1, whereby these various steps are provided for.

The starting lever 6, with its connection to the motor starting switch (not shown), and the slotted member, and its connections to the master cam and to the pump valve, is shown in the diagram of Fig. 1 substantially as it appears in the mechanism. The auxiliary control lever 4 and 1ts connections have been described in full.

The master cam is formed by means of rooves which have been marked 15 on a slide in a suitable groove in the machine base. It has a rackwhich has been indicated at 16d for operating it, said rack being driven by a gear 160 located on a cross shaft 16a. i

This cross shaft is used because the cross head 14 of the master cylinder 12 is at the rearof the machine. The cross head is connected to a rack marked 16 (Fig. 10) by means of a stud on the rack engaging a slotted portion'of the cross head. The rack is slidably held in the machine base as in the instance of the bar 108, and hence moves to and fro with the cross head. The rack 16 and reverse position to the-pump valve.

In order to permit of adjustment at one end of the stroke we provide for an extension 109 for the mid rib of the cam structure, said extension being of the same rib form, and be- 'ing slotted and held in place by a screw.

The mechanism of the hydraulic system is shown in general. assembly in Figs. 2 and 3, and the details of the'cylinder'and pistons carried .by the cam operated frames or carriers, together with the oil connections and valves, are shown in Figs.'5,' 6, 7 and 8.

Referring first to the general assembly,

there are in this case five cylinders 11a grouped in a suitable case, the piston rod 13a of the pistons 11 being connected to the cross head 14, preferably by means of nuts and threaded ends, as will be obvious without.

particular illustration. The cross head is guided by means of the set of piston rods 13a which are individually connected to the cross head.

Instead of the pipes shown in the diagram,

,the main oil chest 53a is provided with passageways here numbered 53 and 54. As shown in Fig. 5 and Fig. 6, the numbers on the several pipes and valves correspond to the numbers in the diagram and need not be again described.

The flexible connection to the cylinder 24,

which is provided for each cylinder, thus perquitting the said cylinder to move with the carriers. is provided for either by flexible pressure tubing or by some type of jointed arm, of which we have shown an illustration.

This arm is formed of a set of tapered plugs 26a, 38, and 36, which have sleeved onto them the two arms 37 and 39. The plug 36 has in addition a sleeved connection with the mem.- ber 32 which is fixed except for a mounting which permits of motion in two planes. This motion is provided for by three bearings 33, 34, and 35, as shown, which are held together by means of pins driven through the assembly and having a peripheral keying action within each of the hearings or the arms extending therefrom, as shown in Fig. 8. The several plugs andarms of the jointed conduit element are held together by means of nuts 43 screwed -qein tothe ends of the tapered plugs. 1

The eyes 44, by means of which the pistons 25 in the carrier cylinders 24, are coupled to the bifurcated ends of the operating arms, are indicated in Figs. 5 and 6.

The operation of the machine is as follows :-A shaft to be turned, which shaft has its journals in proper condition for engagement by the steady rests, is mounted in the spindle chucks, and the several steady rests (Figs. 22 and 23) are adjusted, if need be, by the use of the set screws to get a true center support for the shaft, and a proper abutment at the sides with the carrying members.

The proper tools having been placed in the tool slides in the several carrying frames, and

the amount of turning having been calculated,

: justments will be made for one job, and more ly watched to take care of any looseness' or wear on the parts.

I The crank pins on the shaft to be turned will revolve alike to the carrying members, due to prearranged nature of the two eccentric shafts, and tendency of the carrying frames:

to bind, because of someslight irregularities, and hence cause uneven action on the tools, will be avoided because of the pivotal connection between the carrying frames and the up per eccentric shaft.

The oil feed pump is intended to be operated continuously, and for each operation the machine motor is started by throwing the lever 6 to the left (Fig. 1) and then back toward the right to full running position. This will set the crank shaft to be turned into 1110-. tion, with its axis of rotation central with the spindles. The starting and full running position of the motor switch in theparticular illustrated instance is arranged so that theneutral is at the center, the starting position at the far left and the full running position intermediate the two, and also at the left. This is familiar practice.

The operator will then have freed the lever lfor motion because the stud Go on the lever 6 will be in the main slot in the plate 60. He will push the handle 4: to the left, which will raise the stud or roller 6h in the terminal vertical cam slot in the control cam, which will be-accompanied byan opening of the pump valve 8 to a position of delivering oil at maximum quantity, and will give a rapid traverse to the tools.

The oilwill move the pistons in the master cylinder 12 which will result in the cross head 1 setting the control cam into motion, which takes place at once. Since the roller 6h has been moved to the top of the cam,

the operator will not have to touch the handle 4 after starting up the mechanism, because the cam will thereafter control the position of the valve.

It will be noted also that the operator can.-

. not move the lever 4 in a starting movement until the motor has been brought to full run ning condition.

' The cross head of the master piston operates the series of pistons 11, which act as individual oil pumps to deliver oil to the working cylinders on the several carrying frames. The pistons 25 in the working cylinders move the actuating arms, whose toothed ends move the several tool slides.

As the control cam is moved it causes a motion of the rod 6e,and provides for a rapid tool movement toward the work, then for a working out of the checking tools which is fairly rapid, then a feeding movement which is slow, followed by a rapid return movement of the tool slides to starting position, the last movement of the control cam being one which shuts off the valve 3. This rapid return movement takes place after the cam has rocked the plate (is sufficiently to throw the motor control lever to neutral or stopped position of the motor switch. The operator, by depressing the dog in the lever 4, can rock the lever to a position to shut off the valve, or return the tools by rapid traverse to starting position, even when the cam is in a running position, which provides a safety tool stop.

The stops are arranged so that the tools stop prior to the action of the control cam which stops the spindles and shuts the control valve. This causes no breakage of mechanical parts because the result is merely to build up pressure, which opens the check valves, and it serves a very useful purpose because the tools after the feed has-stopped will still take a very fine film of metal from the work and remove tool marks and give a highly finished result.

During this pause of the tools, the full oil pressure is upon the tools, as has been stated, and until. the control cam completes its travel and reverses the direction of travel for the tools, the excess pressure is by-passed by the relief valves.

A pause of the tools with full working pressure against them would not be possible in a direct mechanical drive, as there would be no relief for the pressures being built up, but with our hydraulic system excess pressures above the working pressure may be dissipated and the tools held against a stop in sizing relationship to the work until the control cam reaches its reversing point.

We have not shown various modifications of our structure, and have given merely a' single concrete illustration of our invention,

' but it will be understood that modifications,

different arrangements, substitution of equivalent structure, change in'size of parts and the like, can be employed readily without departing from the spirit of the claims that follow, in which we define the invention inherent in our-disclosures.

Having thus described our invention, what we claim as new and desire to secure by Let-- tors Patent, is

1. In a crank shaft lathe, the combination of means for revolving a crank shaft to be turned upon. its axis, a plurality of carrying members, tools in said members, means for moving the carrier members in the paths traversed by a plurality of the crank pins of the shaft to be turned, hydraulic mechanisms on the carrying members and movable therewith, means whereby said mechanisms move the tools, and flexible connections leading a hydraulic fluid to the hydraulic mechanisms. 2. In a crank shaft lathe, the combination of means for revolving a crank shaft to be turned upon its axis, a plurality of carrying members, tools-in said members, means for ,moving the carrier members in the paths traversed by a plurality of the crank pins of the shaft to .be turned, hydraulic mechanisms on the carrying members, means whereby said mechanisms move the tools, and flexible connections leading a hydraulic fluid to the hydraulic mechanisms, a series of hydraulic pumps and means for operating the same, said pumps being connectedto said flexible connections.

3. In a crank shaft lathe, the combination of means for revolving a crank shaft to be turned upon its axis, a plurality of carrying members, tools in'sa'id members, means for moving the carrier members in the paths traversed by a plurality of the crank pins of the shaft to be turned, hydraulic mechanisms on the carrying members, means whereby said mechanisms move the tools, and flexible connections leading a hydraulic fluid to the hydraulic mechanisms, a series of hydraulic pumps and means for operating the same, said pumps being connected to said flexible connections, said operating means com risin a sin le member connected to mounted on the said extension, whereby rotation of said gear means Wlll move the tools toward each other or away from each other, said tool supporting bars arranged to slide one on the top of the other, and confined laterally'by said mounting means, said bars being confined vertically by a gib bearing on the edge of one of the bars.

5. I11 combination with a mounting means, a tool supporting bar having rack teeth thereon, another tool supporting bar having rack teeth thereon facing the rack teeth of the first bar, and gear means on the mounting means engaging both sets of teeth, the one bar extending beyond the other, and means for mounting a tool on said extension of the one bar, and a tool on said other bar so as to oppose the tool mounted on the said extension, whereby rotation of said gear means will move the tools toward each other'or away from each other, said tool supporting bars arranged to slide one on the top of the other, and confined laterally by said mounting means, one of said bars having an abutment to engage a stop, and a stop on the mount ing means.

6. In combination with a mounting means, a tool supporting bar having rack teeth thereon, another tool supporting bar having rack teeth thereon facing therack teeth of the first bar, and gear means on the mounting means engaging both sets of teeth, the one bar extending beyond the other, and means for mounting a tool on said extension of the one bar, and a tool on saidother bar soas to oppose thetoollmounted on the said extension whereby rotation of said gear means willmove the tools toward each other or away from each other, said tool supporting bars arranged to slide one on the top of the other, and confined laterally by said mounting means, one of said bars having an abutment to engage a stop, and a stop on the mount I ing means, said stop formed as a gib so supported as to engage the top of the upper one of said bars.

7 In combination. with a mounting means, a tool supporting bar having rack teeth thereon, another tool supporting bar having rack teeth thereon facing the rack teeth of the first bar, and gear means on the mounting means engaging both sets of teeth, the one bar extending beyond the other, and means for mounting a tool on said extension of the one bar, and a tool on said other bar so as to oppose the tool mounted on the said extension, whereby rotation of 'said' gear means will move the tools toward each other 'or away from each other, said tool support- =ing bars arranged to slide one on the top of the other, and confined laterally by said mounting means, one of said bars having an abutment to engage a stop, and a stop on the mounting means, said stop formed as a gib so supported as to engage the top of the upper one of said bars, and means for adjusting said gib lengthwise to regulate the stopped position of thetool bars.

8. In a lathe the combination with a frame, of means thereon for engaging and rotating a crank shaft on its axis so that the crank pins move in an eccentric path, a series of carrier members some in contact and some intel-spaced from each other, means for moving said carriers eccentrieally with the crank pins, tools mounted 111 said carriers, and spacing means mounted on the frame and lying between the spaced carrier members and rier members some in Contact and some interspaced from each other, means for moving said carriers eccentrically with the (rank pins, tools mounted in said carriers. and spacing members mounted on the frame and lying between the spaced carrier members and in bearing engagement therewith, some at least of saidspacing members embodying steady rest means for the crank shaft.

10. In a lathe the combination with a frame, of means thereon for engaging and rotating a crank shaft on its axis so that the crank pins move in an eccentric path, a series of carrier members some in contact and some interspaced from each other, means for moving said carriers eecentrically with the crank pins, tools mounted in said carriers, and sp'ac- I frame, of means thereon for engaging and rotating a crank shaft on its axis so that the crank pins move in an eccentric path, a series of carrier members, means for moving said carrier members eccentrically with the crank pins, and .tool supporting members arranged in the carriers so that each carrier member has a plurality of tools to engage the pins to be turned from opposite sides, and means for actuating the tool supporting members comprising an operating mechanism on the carriers, a source of power, and means for connecting said source of power flexibly to said operating mechanism;

12. In a crank shaft lathe having eccentrically moving means thereon for turning a series of crank pins of a crank shaft revolving on its axis, a hydraulic driving mechanism for the tools in said eccentrically moving means, and means for supplying hydraulic power thereto comprising a control valve, and a master piston, and automatic means operated by the piston to shift the control valve, including a cam element.

13. In a crank shaft lathe having eccentrically moving means thereon for turning a series of crank pins of a crank shaft revolving on its axis, a hydraulic driving mechanism for the tools in said eccentrically moving means, and means for supplying hydraulic power theretocomprising a control valve, and a master piston, and automatic means operated by the pistonto shift the than predetermined relation.

14. In a lathe thecombination with a frame, of means thereon for engaging and rotating a crank shaft on its axis so that the crank pins move in an eccentric path, a series of carrier members, means for movin said carrier members eccentrically with the crank pins, and tool supporting members arranged in the carriers so that each carrier member has a plurality of tools to engage the pins to beturnedfrom opposite sides, and

means for actuating the tool supporting members comprising an operating mechanism on the carriers, a source of power, and means for connecting said source of power flexibly to said operating mechanism, said source of power having a main unitary power delivery means, and a series of auxiliary power delivery means operated by the main means, one for each carrier.

15. In a lathe the combination with a frame, of means thereon for engaging and rotating a crank shaft on its axis so that the crank pins move in an eccentric path, a series of carrier members, means for moving said carrier members eccentrically with the crank pins, and tool supporting means on the carriers, .tool feeding means supported on the carriers, and comprising hydraulic elements connected to said feeding means, and flexible passageways supplied with fluid under pressure for applying a source of power to each tool feeding means.

16. In a lathe the combination with a frame, of means thereon for engaging and rotating a crank shaft on its axis so that the crank pins move in an eccentric path, a series of carrier members, means for moving said carrier members eccentrically with the crank pins, and tool supporting means on the earriers, toolfeeding means on the carriers, and comprising hydraulic elements connected to said feeding means, and flexible means for applying a source of power to each tool feedv ing means, said source of power having a .main power delivery means, and a series of auxiliary power delivery means operated by the main means, one for each carrier.

17. In a lathe the combination with a frame, of means thereon for engaging and rotating a crank shaft on its axis so that the crank pins move in an eccentric path, a series of carrier members, means for moving said carrier members eccentrically with the crank pins, and tool supporting means on the car riers, and tool feeding means on the carriers, includin hydraulic cylinders and pistons, and flexible conduits for delivery of fluid to said cylinders, a main source of supply of fluid, and a series of auxiliary fluid supply means operated from the main source, one for each hydraulic cylinder.

18. In a lathe the combination with a frame, of means thereon for engaging and rotating a crank shaft on its axis so that the crank pins move in an eccentric path, a series of carrier members, means for moving said carrier memberseccentrically with the crank pins, and tool supporting means on the carriers, and tool feeding means on the carriers,

g including hydraulic cylinders and pistons,

and flexible conduits for delivery of fluid to said cylinders, a main source ofsupply of fluid, and a series of auxiliary fluid supply means operated from the main source, one for each hydraulic cylinder, and means for controlling the rate'of flow of fluid from the main source.

19. In a lathe the combination with a frame, of means thereon for engaging and rotating a crank shaft on its axis so that the crank pins move in an eccentric path, a series of carrier members, means for moving said carrier members eccentrically with the crank pins, and tool supporting means on the carriers, and tool feeding means on the carriers,

including hydraulic cylinders and pistons,-

and flexible conduits for delivery of fluid to said cylinders, a main source of supply of fluid, and a series of auxiliary fluid supply means operated from the main source, one for each hydraulic cylinder, and automatic mech- 

